WO2013022038A1 - 制御装置 - Google Patents
制御装置 Download PDFInfo
- Publication number
- WO2013022038A1 WO2013022038A1 PCT/JP2012/070251 JP2012070251W WO2013022038A1 WO 2013022038 A1 WO2013022038 A1 WO 2013022038A1 JP 2012070251 W JP2012070251 W JP 2012070251W WO 2013022038 A1 WO2013022038 A1 WO 2013022038A1
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- WIPO (PCT)
- Prior art keywords
- control
- mode
- clutch
- control mode
- electrical machine
- Prior art date
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Images
Classifications
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- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/70—Energy storage systems for electromobility, e.g. batteries
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/7072—Electromobility specific charging systems or methods for batteries, ultracapacitors, supercapacitors or double-layer capacitors
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/72—Electric energy management in electromobility
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S903/00—Hybrid electric vehicles, HEVS
- Y10S903/902—Prime movers comprising electrical and internal combustion motors
Definitions
- the present invention controls a vehicle drive device in which a first engagement device, a rotating electrical machine, and a second engagement device are provided in order from the internal combustion engine side in a power transmission path that connects the internal combustion engine and wheels. It relates to a control device.
- Patent Document 1 As a conventional technique of the control device as described above, for example, there is a technique described in Patent Document 1 below. In the description of the background art section, the member names in Patent Document 1 are quoted in [].
- the control device generates power in the rotating electrical machine [motor generator MG] in the direct engagement state of the first engagement device [first clutch CL1] and in the slip engagement state of the second engagement device [second clutch CL2].
- the WSC positive power generation mode can be realized.
- the rotating electric machine In the WSC positive power generation mode, the rotating electric machine can be caused to generate electric power using the driving force while driving the vehicle using the driving force of the internal combustion engine [engine E].
- a vehicle drive device in which a first engagement device, a rotating electrical machine, and a second engagement device are sequentially provided from a side of the internal combustion engine on a power transmission path that connects the internal combustion engine and wheels.
- the characteristic configuration of the control device to be controlled includes a first control mode in which the rotating electrical machine generates power in the slip engagement state of both the first engagement device and the second engagement device, and the first engagement mode.
- a second control mode for causing the rotating electrical machine to generate power in a direct engagement state of both the combined device and the second engagement device, a direct engagement state of the first engagement device, and a second engagement device.
- a third control mode for causing the rotating electrical machine to generate power in a slip engagement state, and a power generation for the rotating electrical machine in a slip engagement state of the first engagement device and a direct engagement state of the second engagement device A fourth control mode, a mode control unit for switching, and the second control mode
- a target amount acquisition unit that acquires at least one of a temperature and a calorific value of the combined device as a selection target amount, and the mode control unit from the second control mode and the second control mode from the first control mode
- the mode shift is executed via the third control mode, and the selection target amount is If it is greater than or equal to the selection reference value, the mode transition is executed through the fourth control mode.
- the “rotary electric machine” is used as a concept including any of a motor (electric motor), a generator (generator), and a motor / generator functioning as both a motor and a generator as necessary.
- the “directly engaged state” represents a state in which the two engaging members engaged by the target engaging device are engaged with each other, and the “slip engaged state” A state in which the two engaging members are engaged so as to be able to transmit a driving force in a state having a rotational speed difference is shown.
- the first control mode in which the rotating electrical machine can generate power in the slip engagement state of both the first engagement device and the second engagement device can be realized.
- the difference in rotational speed between the combined members can be reduced for both the first engagement device and the second engagement device, and the amount of heat generated is suppressed for both the first engagement device and the second engagement device. be able to. Therefore, the first control mode for causing the rotating electrical machine to generate power can be realized under a relatively large number of situations, and it becomes easy to secure a desired power generation amount.
- in the mode transition of the at least any one direction side between the 1st control mode and the 2nd control mode it is based on the magnitude relationship between the selection object amount and the selection reference value.
- the passing mode from the third control mode and the fourth control mode it is possible to appropriately select the passing mode from the third control mode and the fourth control mode. That is, when the temperature increase of the second engagement device is allowed, the third control mode in which the torque of the internal combustion engine can be directly transmitted to the rotating electrical machine is selected to improve the energy efficiency.
- the fourth control mode can be selected to suppress the amount of heat generated by the second engagement device. Accordingly, the transition to the first control mode or the transition from the first control mode to the other mode that facilitates securing a desired power generation amount while protecting the second engagement device is appropriately executed. Can do.
- the target amount acquisition unit acquires at least one of the temperature and the heat generation amount of the first engagement device as a first determination target amount, and at least one of the temperature and the heat generation amount of the second engagement device.
- the first determination target amount is less than a predetermined first determination reference value
- the second determination target amount is a predetermined second If it is less than the determination reference value, control is performed according to the required driving force so that the required driving force required to drive the wheel is transmitted to the wheel, and in the first control mode,
- the driving force transmitted to the wheel is the request.
- the control for reducing the output torque of the internal combustion engine it is preferable to perform the control for reducing the output torque of the internal combustion engine.
- the output torque of the internal combustion engine is reduced to reduce the first determination target value.
- the transmission torque can be reduced for both the engagement device and the second engagement device. Therefore, the amount of heat generated by both engagement devices can be reduced and temperature rise can be suppressed.
- the target amount acquisition unit acquires at least one of a temperature and a heat generation amount of the first engagement device as a first determination target amount, and the first determination target amount is predetermined in the first control mode.
- the power generation amount by the rotating electrical machine is reduced by reducing the output torque of the rotating electrical machine, and the internal combustion engine is reduced according to the decrease in the output torque of the rotating electrical machine. It is preferable to execute control for reducing the output torque of the engine.
- the transmission torque of the first engagement device can be decreased according to the decrease in the output torque of the internal combustion engine.
- the amount of heat generated by the first engagement device can be reduced to suppress the temperature rise.
- a control device 40 is a vehicle whose control target is a drive device 1 for driving a vehicle 6 (hybrid vehicle) including both an internal combustion engine 11 and a rotating electrical machine 12. It is a control device for a motor drive device.
- the drive device 1 and the control device 40 according to the present embodiment will be described in order.
- drive connection means a state in which two rotating elements are connected so as to be able to transmit a driving force, and a state in which the two rotating elements are connected so as to rotate integrally
- the two rotating elements are used as a concept including a state in which a driving force can be transmitted via one or more transmission members.
- a transmission member includes various members (for example, a shaft, a gear mechanism, a belt, a chain, etc.) that transmit rotation at the same speed or with a variable speed.
- driving force is used synonymously with “torque”.
- engagement pressure for each engagement device represents a pressure that presses the two engagement members engaged by the engagement device, for example, by a hydraulic servo mechanism or the like.
- release pressure represents a pressure at which the engagement device is constantly released (a state in which rotation and driving force are not transmitted between the two engagement members engaged by the engagement device).
- Release boundary pressure represents a pressure (release side slip boundary pressure) at which the engagement device enters a slip boundary state at the boundary between the released state and the slip engagement state.
- engagement boundary pressure represents a pressure (engagement side slip boundary pressure) at which the engagement device enters a slip boundary state between the slip engagement state and the direct engagement state.
- Complete engagement pressure represents a pressure at which the engagement device is steadily in a direct engagement state.
- the drive device 1 to be controlled by the control device 40 is configured as a drive device for a so-called 1-motor parallel type hybrid vehicle.
- the drive device 1 has a first clutch C1, a rotating electrical machine 12, and a second clutch C2 (in order from the side of the internal combustion engine 11 to a power transmission path connecting the internal combustion engine 11 and the wheels 15 in order.
- a transmission mechanism 13 is provided. That is, the rotary electric machine 12 is provided in the power transmission path connecting the internal combustion engine 11 and the wheel 15, and the first clutch C ⁇ b> 1 is provided between the internal combustion engine 11 and the rotary electric machine 12. Is provided with a second clutch C2 (transmission mechanism 13).
- the internal combustion engine 11 is a prime mover that is driven by combustion of fuel inside the engine to extract power, and for example, a gasoline engine or a diesel engine can be used.
- the internal combustion engine 11 is drivingly connected to the input shaft I.
- the output shaft of the internal combustion engine such as a crankshaft of the internal combustion engine 11 and the input shaft I rotate integrally.
- the first clutch C1 is provided so as to be able to release the drive connection (transmission of drive force) between the internal combustion engine 11 and the rotating electrical machine 12.
- the first clutch C1 is a friction engagement device that selectively connects the input shaft I, the intermediate shaft M, and the output shaft O (in other words, selectively connects the internal combustion engine 11, the rotating electrical machine 12, and the wheels 15). And functions as an internal combustion engine disconnecting clutch that disconnects the internal combustion engine 11 from the wheel 15.
- a wet multi-plate clutch, a dry single-plate clutch, or the like can be used.
- the first clutch C1 corresponds to the “first engagement device” in the present invention.
- the rotating electrical machine 12 includes a rotor and a stator (not shown), and the rotor of the rotating electrical machine 12 is drivingly connected to the intermediate shaft M.
- the intermediate shaft M functions as a rotor shaft of the rotating electrical machine 12, and the rotor and the intermediate shaft M rotate integrally.
- the rotating electrical machine 12 is electrically connected to a power storage device 28 such as a battery or a capacitor via an inverter device 27.
- the rotating electrical machine 12 receives power from the power storage device 28 and powers, or supplies power generated by the output torque of the internal combustion engine 11 (internal combustion engine torque Te) or the inertial force of the vehicle 6 to the power storage device 28. Accumulate electricity.
- the intermediate shaft M as the rotor shaft is an input shaft (transmission input shaft) of the transmission mechanism 13.
- the transmission mechanism 13 is an automatic stepped transmission mechanism that can switch a plurality of shift stages having different transmission ratios.
- the speed change mechanism 13 forms a plurality of shift speeds so that a gear mechanism such as a planetary gear mechanism and a plurality of engagement devices such as clutches and brakes for engaging or releasing the rotation elements of the gear mechanism (this example) The friction engagement device).
- a wet multi-plate clutch or the like can be used as the plurality of engaging devices.
- the plurality of engagement devices include the second clutch C2, and other clutches, brakes, and the like are included.
- the second clutch C2 corresponds to the “second engagement device” in the present invention.
- the speed change mechanism 13 changes the rotational speed of the intermediate shaft M (the speed change input shaft) based on the speed ratio set for each speed step formed according to the engagement state of the plurality of speed change engagement devices.
- the torque is converted and transmitted to the output shaft O as the output shaft (shift output shaft) of the transmission mechanism 13.
- the “transmission ratio” is the ratio of the rotational speed of the intermediate shaft M (transmission input shaft) to the rotational speed of the output shaft O (transmission output shaft).
- Torque transmitted from the speed change mechanism 13 to the output shaft O is distributed and transmitted to the left and right wheels 15 via the output differential gear unit 14.
- the drive device 1 can cause the vehicle 6 to travel by transmitting the torque of one or both of the internal combustion engine 11 and the rotating electrical machine 12 to the wheels 15.
- the driving device 1 includes an oil pump (not shown) that is drivingly connected to the intermediate shaft M.
- the oil pump is driven by the driving force of one or both of the rotating electrical machine 12 and the internal combustion engine 11 to generate hydraulic pressure.
- the oil from the oil pump is adjusted to a predetermined oil pressure by the oil pressure control device 25 and then supplied to the first clutch C1, the second clutch C2, and the like.
- an oil pump having a dedicated drive motor may be provided.
- the vehicle 6 includes an input shaft rotational speed sensor Se1, an intermediate shaft rotational speed sensor Se2, and an output shaft rotational speed sensor Se3.
- the input shaft rotational speed sensor Se1 is a sensor that detects the rotational speed of the input shaft I.
- the rotational speed of the input shaft I detected by the input shaft rotational speed sensor Se1 is equal to the rotational speed of the internal combustion engine 11.
- the intermediate shaft rotation speed sensor Se2 is a sensor that detects the rotation speed of the intermediate shaft M.
- the rotational speed of the intermediate shaft M is equal to the rotational speed of the rotor of the rotating electrical machine 12, and is also equal to the rotational speed of the transmission input shaft. Therefore, for example, a rotation sensor (resolver or the like) provided in the rotating electrical machine 12 or a speed change input sensor (pulse type detector or the like) provided in the transmission mechanism 13 can be used as the intermediate shaft rotation speed sensor Se2.
- the output shaft rotation speed sensor Se3 is a sensor that detects the rotation speed of the output shaft O. Since the rotational speed of the output shaft O is equal to the rotational speed of the transmission output shaft, the output shaft rotational speed sensor Se3 can use, for example, a transmission output sensor (pulse type detector or the like) provided in the transmission mechanism 13.
- the control device 40 derives the vehicle speed that is the traveling speed of the vehicle 6 based on the rotational speed of the output shaft O detected by the output shaft rotational speed sensor Se3.
- a control device 40 includes a travel mode determination unit 41, a required driving force determination unit 42, a rotating electrical machine control unit 43, a first clutch operation control unit 44, and a speed change mechanism.
- An operation control unit 45, a target amount acquisition unit 51, a mode control unit 52, a target amount determination unit 53, and a torque correction control unit 54 are provided. Each of these functional units is configured to exchange information with each other.
- the control device 40 includes an arithmetic processing device such as a CPU as a core, and includes a storage device such as a RAM and a ROM. Each functional unit of the control device 40 is configured by software (program) stored in a ROM or the like, hardware such as a separately provided arithmetic circuit, or both. In addition, about the function part comprised by a program, the arithmetic processing apparatus with which the control apparatus 40 is provided operate
- the vehicle 6 includes an internal combustion engine control device 30 that controls the operation of the internal combustion engine 11.
- the internal combustion engine control device 30 and the control device 40 are configured to be able to exchange information with each other.
- the internal combustion engine control device 30 controls the operating point (internal combustion engine torque Te and rotational speed) of the internal combustion engine 11 based on a command from the control device 40.
- the control device 40 is configured to be able to acquire information on detection results by the above-described input shaft rotation speed sensor Se1, intermediate shaft rotation speed sensor Se2, and output shaft rotation speed sensor Se3, and an accelerator pedal (not shown).
- the sensor that detects the amount of operation (or accelerator opening), the sensor that detects the amount of operation of the brake pedal (not shown), the sensor that detects the state of the power storage device 28 (the amount of storage, temperature, etc.), etc. Information can also be acquired.
- the travel mode determination unit 41 is a functional unit that determines the travel mode of the vehicle 6.
- the travel mode determination unit 41 determines a travel mode to be realized by the drive device 1 by referring to a predetermined map (mode selection map) based on, for example, the vehicle speed, the accelerator opening, the power storage amount of the power storage device 28, and the like. To do.
- the driving modes that can be selected by the driving mode determination unit 41 include an electric driving mode and a parallel driving mode.
- the rotating electrical machine 12 basically runs with the output torque (rotating electrical machine torque Tm) only when the first clutch C1 is disengaged and the second clutch C2 is directly engaged.
- Tm rotating electrical machine torque
- the parallel travel mode both the first clutch C1 and the second clutch C2 are directly engaged, the first clutch C1 and the second clutch C2 are both in the slip engagement state and the other is in the direct engagement state, or the first clutch.
- the vehicle 6 is basically caused to travel by at least the internal combustion engine torque Te.
- the rotating electrical machine 12 In the parallel traveling mode, in addition to the traveling mode in which the rotating electrical machine 12 outputs a torque in the positive direction (powering direction) to assist the driving force by the internal combustion engine torque Te, the rotating electrical machine 12 has a torque in the negative direction (power generation direction).
- a travel mode in which (regenerative torque) is output and electric power is generated by a part of the internal combustion engine torque Te is included.
- the parallel control mode (power generation mode) in which the vehicle 6 travels while generating electric power in the rotating electrical machine 12 using the internal combustion engine torque Te includes a first control mode, a second control mode, a third control mode, And a fourth control mode.
- the rotating electrical machine 12 In the first control mode, the rotating electrical machine 12 generates power in the slip engagement state of both the first clutch C1 and the second clutch C2.
- the rotating electrical machine 12 In the second control mode, the rotating electrical machine 12 generates power in a state where both the first clutch C1 and the second clutch C2 are directly connected.
- the rotating electrical machine 12 generates power in the direct engagement state of the first clutch C1 and the slip engagement state of the second clutch C2.
- the fourth control mode the rotating electrical machine 12 generates power in the slip engagement state of the first clutch C1 and the direct engagement state of the second clutch C2.
- the required driving force determination unit 42 is a functional unit that determines the required driving force Td that is required to drive the wheels 15 to drive the vehicle 6.
- the required driving force determining unit 42 determines the required driving force Td by referring to a predetermined map (requested driving force determination map) based on the vehicle speed and the accelerator opening.
- the required driving force Td determined in this way is basically equal to the driving force necessary for realizing the behavior according to the driver's artificial operation (for example, accelerator operation).
- the shared driving force that each of the internal combustion engine 11 and the rotating electrical machine 12 takes is determined so that the sum of the respective divided driving forces becomes equal to the required driving force Td.
- control of the internal combustion engine 11 by the internal combustion engine control device 30 and control of the rotating electrical machine 12 by the rotating electrical machine control unit 43 are executed so that the determined shared driving force is transmitted to the wheels 15.
- the driving force having the same magnitude as the required driving force Td is transmitted to the wheel 15.
- the rotating electrical machine torque Tm is a negative torque (hereinafter referred to as “required regenerative torque”) required to generate the required power generation amount. Is set.
- the shared driving force for the rotating electrical machine 12 since the shared driving force for the rotating electrical machine 12 has a negative value, the shared driving force for the internal combustion engine 11 has a value larger than the required driving force Td.
- the rotating electric machine control unit 43 is a functional unit that controls the operation of the rotating electric machine 12.
- the rotating electrical machine control unit 43 controls the operating point (the rotating electrical machine torque Tm and the rotational speed) of the rotating electrical machine 12 by controlling the inverter device 27.
- the rotating electrical machine control unit 43 can switch between torque control and rotational speed control of the rotating electrical machine 12 according to the traveling state of the vehicle 6.
- the torque control is a control in which a target torque is set as a control target and the rotating electrical machine torque Tm is made to follow (approach) the target torque.
- the rotational speed control is a control in which a target rotational speed is set as a control target, and the rotating electrical machine torque Tm is controlled so that the rotational speed of the rotating electrical machine 12 follows the target rotational speed.
- the first clutch operation control unit 44 is a functional unit that controls the operation of the first clutch C1.
- the first clutch operation control unit 44 controls the hydraulic pressure supplied to the first clutch C1 via the hydraulic pressure control device 25, and controls the engagement pressure of the first clutch C1, whereby the first clutch C1 operation control is performed.
- the engagement pressure is set to be equal to or higher than the engagement boundary pressure (for example, complete engagement pressure).
- the first clutch C1 is brought into a direct engagement state.
- the first clutch C1 is brought into the slip engagement state by setting the engagement pressure to the slip engagement pressure not less than the release boundary pressure and less than the engagement boundary pressure.
- the driving force is transmitted from the rotating shaft with the higher rotational speed toward the rotating shaft with the lower rotational speed while the input shaft I and the intermediate shaft M rotate relative to each other.
- the maximum value of torque that can be transmitted in the direct engagement state or slip engagement state of the first clutch C1 is determined according to the engagement pressure of the first clutch C1 at that time.
- the magnitude of the torque (transmission torque) transmitted by the first clutch C1 is equal to the transmission torque capacity in the slip engagement state.
- the engagement pressure and the transmission torque are controlled by continuously controlling the amount of oil supplied to the first clutch C1 and the magnitude of the supply oil pressure with a proportional solenoid or the like in accordance with the oil pressure command for the first clutch C1. Increase / decrease in capacity can be controlled continuously.
- the first clutch operation control unit 44 can switch between torque control and rotation speed control of the first clutch C1 in accordance with the traveling state of the vehicle 6.
- the torque control is a control in which a target transmission torque capacity is set as a control target and the transmission torque capacity of the first clutch C1 follows the target transmission torque capacity.
- the rotational speed control sets a target differential rotational speed, a rotational speed of the input side rotational member (input side engaging member), or a rotational speed of the output side rotational member (output side engaging member) as a control target,
- the engagement pressure (hydraulic pressure) and transmission torque capacity of the first clutch C1 By controlling the engagement pressure (hydraulic pressure) and transmission torque capacity of the first clutch C1, the rotational speed difference between the two engagement members engaged by the first clutch C1 (in this example, the input shaft I and the intermediate shaft) M), the rotation speed of the input side rotation member (in this example, the input shaft I), or the rotation speed of the output side rotation member (in this example, the intermediate shaft M) is made to follow the control target. Control.
- the transmission mechanism operation control unit 45 is a functional unit that controls the operation of the transmission mechanism 13.
- the transmission mechanism operation control unit 45 determines a target gear position by referring to a predetermined map (shift map) based on the accelerator opening and the vehicle speed. Then, the transmission mechanism operation control unit 45 controls the hydraulic pressure supplied to predetermined clutches and brakes provided in the transmission mechanism 13 based on the determined target shift stage to form the target shift stage.
- the second clutch C2 provided in the speed change mechanism 13 cooperates with a brake also provided in the speed change mechanism 13 to form the first speed stage that is the speed ratio of the maximum speed ratio.
- the function unit that controls the operation of the second clutch C2 is specifically referred to as a second clutch operation control unit 45a here.
- the second clutch operation control unit 45a controls the hydraulic pressure supplied to the second clutch C2 via the hydraulic control device 25, and controls the engagement pressure of the second clutch C2, thereby operating the second clutch C2. Take control.
- the basic control and the operation control of the first clutch C1 by the first clutch operation control unit 44 are basically different except that the control target and the matters accompanying it are partially different. Is the same.
- the target quantity acquisition unit 51 is a functional unit that acquires a target quantity B, which is a physical quantity related to the heat generation state of the engagement device. Specifically, the target amount acquisition unit 51 acquires at least one of the temperature and the heat generation amount of the second clutch C2 as the selection target amount B0. In the present embodiment, the target amount acquisition unit 51 further includes the first clutch C1. Is acquired as the first determination target amount B1, and at least one of the temperature and the heat generation amount of the second clutch C2 is acquired as the second determination target amount B2.
- the selection target amount B0 and the second determination target amount B2 may be the same physical amount or different physical amounts.
- the temperature of the first clutch C1 and the second clutch C2 can be obtained based on the detection result of a temperature sensor (not shown). Further, the amount of heat generated in the slip engagement state of the first clutch C1 and the second clutch C2 depends on the rotational speed difference between the two engagement members engaged by the clutch and the transmission torque capacity of the clutch. Based on (for example, based on the product of the rotational speed difference and the transmission torque capacity), it can be configured to be acquired. Note that the clutch temperature may be acquired based on the heat generation amount of the clutch (for example, based on the integrated value of the heat generation amount).
- the target amount determination unit 53 compares the target amount B acquired by the target amount acquisition unit 51 with a reference value D (determination reference value) for the target amount B, and determines a magnitude relationship. Part. In the present embodiment, the target amount acquisition unit 51 acquires three of the selection target amount B0, the first determination target amount B1, and the second determination target amount B2 as the target amount B. Therefore, the target amount determination unit 53 For each of the three target amounts B, the magnitude relation with the corresponding reference value D is determined.
- D determination reference value
- the target amount determination unit 53 determines the magnitude relationship between the selection target amount B0 and a selection reference value D0 that is a reference value D for the selection target amount B0 that is determined in advance. In addition, the target amount determination unit 53 determines the magnitude relationship between the first determination target amount B1 and a first determination reference value D1 that is a reference value D for the first determination target amount B1 that is determined in advance. At the same time, the second determination target amount B2 is subjected to determination of a magnitude relationship with a second determination reference value D2 that is a reference value D for the second determination target amount B2. In the present embodiment, the target amount determination unit 53 further includes a first determination target amount B1 between a predetermined third determination reference value D3 that is a reference value D for the first determination target amount B1. Determine the magnitude relationship.
- the selection reference value D0 and the second determination reference value D2 are set according to, for example, the heat resistance of the second clutch C2, and can be the same value.
- the first determination reference value D1 and the third determination reference value D3 are set according to, for example, the heat resistance of the first clutch C1, and can be set to the same value.
- all target amounts B B0, B1, B2
- all reference values D D0, D1, D2, D3 are set to different values. .
- the second determination reference value D2 is set to a value larger than the selection reference value D0
- the third determination reference value D3 is set to a value larger than the first determination reference value D1, and the smaller side
- the selection reference value D0, the first determination reference value D1, the second determination reference value D2, and the third determination reference value D3 are in the order (D0 ⁇ D1 ⁇ D2 ⁇ D3).
- the reference value D for the target amount B is set for each of the temperature and the heat generation amount.
- both the temperature and the calorific value are equal to or higher than the corresponding reference value D
- a configuration in which the target amount B is determined to be greater than or equal to the reference value D when it is greater than or equal to the reference value D may be employed.
- the mode control unit 52 controls each of the travel modes determined by the travel mode determination unit 41 by cooperatively controlling other functional units such as the first clutch operation control unit 44 and the second clutch operation control unit 45a. Is a functional unit that realizes each mode.
- the travel modes that can be selected by the travel mode determination unit 41 include the first control mode, the second control mode, the third control mode, and the fourth control mode. The first control mode, the second control mode, the third control mode, and the fourth control mode can be switched.
- the control executed by the mode control unit 52 includes a control for executing a first mode transition (refer to specific examples of FIGS. 6 to 8 described later) that is a mode transition from the first control mode to the second control mode. (First mode transition control) and control for executing the second mode transition (refer to specific examples of FIGS. 9 and 10 described later) which is a mode transition from the second control mode to the first control mode (first Two-mode transition control).
- the mode control unit 52 performs the third control mode when the selection target amount B0 is less than the selection reference value D0 during the mode transition of at least one of the first mode transition and the second mode transition (both in this example). Then, the mode transition is executed, and when the selection target amount B0 is equal to or larger than the selection reference value D0, the mode transition is executed through the fourth control mode. In this embodiment, based on the selection target amount B0 at the start of execution of the first mode transition control and the second mode transition control, the mode transition is executed via any control mode of the third control mode and the fourth control mode. Decide what to do.
- step # 01: Yes the target amount determination unit 53 determines the magnitude relationship between the selection target amount B0 and the selection reference value D0 (Ste # 02).
- Step # 02 the target amount determination unit 53 determines that the selection target amount B0 is less than the selection reference value D0 (step 02: Yes)
- control for shifting the first clutch C1 to the direct engagement state is started. (Step # 03).
- step # 04: No Until the first clutch C1 is in the direct engagement state (step # 04: No), this transition control is continuously executed (step # 03), and when the first clutch C1 is in the direct engagement state (step # 03). Step # 04: Yes), the transition from the first control mode to the third control mode is completed.
- step # 05 After the transition to the third control mode is completed, control for shifting the second clutch C2 to the direct engagement state is started (step # 05). Until the second clutch C2 is in the direct engagement state (step # 06: No), this transition control is continued (step # 05), and when the second clutch C2 is in the direct engagement state (step # 05). Step # 06: Yes), the transition from the third control mode to the second control mode is completed, and the first mode transition control ends.
- step 02: No when the target amount determination unit 53 determines that the selection target amount B0 is greater than or equal to the selection reference value D0 (step 02: No), as shown in FIG. 2, the above-described steps # 03 to # 06 are performed.
- the process (step # 07 to step # 10) in which the first clutch C1 and the second clutch C2 are switched is sequentially executed, and the first control mode via the fourth control mode is changed to the second control mode. Transition takes place.
- the transition of the first clutch C1 from the slip engagement state to the direct engagement state and the transition of the second clutch C2 from the slip engagement state to the direct engagement state are executed.
- the selection target amount B0 is less than the selection reference value D0
- the transition to the direct engagement state is executed in the order of the first clutch C1 and the second clutch C2
- the selection target amount B0 is selected as the selection reference.
- the transition to the direct engagement state is executed in the order of the second clutch C2 and the first clutch C1.
- the time during which the first clutch C1 is in the slip engagement state (hereinafter referred to as “slip time”) when the first mode transition control is executed is when the selection target amount B0 is less than the selection reference value D0. It becomes shorter than the slip time of the second clutch C2, and becomes longer than the slip time of the second clutch C2 when the selection target amount B0 is equal to or larger than the selection reference value D0.
- step # 11 From the second control mode in which both the first clutch C1 and the second clutch C2 are in the direct engagement state, to the first control mode in which both the first clutch C1 and the second clutch C2 are in the slip engagement state
- step # 12 the target amount determination unit 53 determines the magnitude relationship between the selection target amount B0 and the selection reference value D0 ( Step # 12).
- step # 12 the control for shifting the second clutch C2 to the slip engagement state is performed. Start (step # 13).
- step # 14: No Until the second clutch C2 is in the slip engagement state (step # 14: No), this transition control is continuously executed (step # 13), and when the second clutch C2 is in the slip engagement state (step # 13). Step # 14: Yes), the transition from the second control mode to the third control mode is completed.
- step # 15 After the transition to the third control mode is completed, control for shifting the first clutch C1 to the slip engagement state is started (step # 15). Until the first clutch C1 is in the slip engagement state (step # 16: No), this transition control is continuously executed (step # 15), and when the first clutch C1 is in the slip engagement state (step # 15). Step # 16: Yes), the transition from the third control mode to the first control mode is completed, and the second mode transition control ends.
- step 12 determines that the selection target amount B0 is greater than or equal to the selection reference value D0 (step 12: No)
- the above-described steps # 13 to # 16 are performed.
- the process (step # 17 to step # 20) in which the first clutch C1 and the second clutch C2 are switched is sequentially executed, and the second control mode via the fourth control mode is changed to the first control mode. Transition takes place.
- the transition from the direct engagement state of the first clutch C1 to the slip engagement state and the transition of the second clutch C2 from the direct engagement state to the slip engagement state are executed.
- the selection target amount B0 is less than the selection reference value D0
- the transition to the slip engagement state is executed in the order of the second clutch C2 and the first clutch C1
- the selection target amount B0 is the selection reference amount.
- the transition to the slip engagement state is executed in the order of the first clutch C1 and the second clutch C2.
- the slip time of the first clutch C1 is the second when the selection target amount B0 is less than the selection reference value D0, as in the first mode transition control.
- the slip time of the second clutch C2 is longer than the slip time of the clutch C2.
- the torque correction control unit 54 is a functional unit that executes torque correction control. In this torque correction control, torque reduction control for reducing the internal combustion engine torque Te when a predetermined condition is satisfied is executed. In the present embodiment, the torque correction control unit 54 executes two torque correction controls of the first torque correction control and the second torque correction control in parallel.
- the first torque correction control will be described with reference to the flowchart of FIG.
- the first determination target amount B1 is not less than the first determination reference value D1 (step # 23: Yes), and the second determination target amount.
- wheel transmission driving force reduction control is executed as torque reduction control (step # 25).
- the first torque correction control is executed during the execution of the first mode transition or the second mode transition (step # 21: Yes).
- the wheel transmission driving force reduction control is executed at most once during the period in which the first control mode is continuously realized.
- the first determination target amount B1 and the second determination target amount B2 are repeatedly acquired by the target amount acquisition unit 51 while the first control mode is realized.
- the driving force transmitted to the wheels 15 (hereinafter referred to as “wheel transmission driving force”) is made smaller than the required driving force Td determined by the required driving force determination unit 42. Further, the control is to reduce the internal combustion engine torque Te. In the specific example of FIG. 8 to be described later, the wheel transmission driving force reduction control is executed at time T23, and the wheel transmission driving force is reduced from the required driving force Td in accordance with the reduction amount of the internal combustion engine torque Te.
- the internal combustion engine torque Te and the rotating electrical machine torque Tm are basically controlled so that the wheel transmission driving force becomes equal to the required driving force Td.
- the required driving force Td determined by the required driving force determination unit 42 is transmitted to the wheels 15.
- step # 34 the second torque correction control is executed during the execution of the first mode transition or the second mode transition (step # 31: Yes).
- step # 31: Yes the power generation amount reduction control is executed at most once during the period in which the first control mode is continuously realized.
- the first determination target amount B1 is repeatedly acquired by the target amount acquisition unit 51 while the first control mode is realized.
- the power generation amount reduction control reduces the amount of power generated by the rotating electrical machine 12 by reducing the rotating electrical machine torque Tm (more precisely, the absolute value of the rotating electrical machine torque Tm) and reduces the amount of decrease in the rotating electrical machine torque Tm.
- the internal combustion engine torque Te is reduced.
- the power generation amount reduction control is executed at time T24, and the internal combustion engine torque Te is reduced according to the reduction amount (reduction amount of the absolute value) of the rotating electrical machine torque Tm from the required regeneration torque. is doing.
- the rotating electrical machine torque Tm is set to zero by the power generation amount reduction control, the amount of decrease in the rotating electrical machine torque Tm from the required regenerative torque is equal to the required regenerative torque.
- the traveling mode is classified as if the rotating electrical machine 12 is generating power. That is, in the example shown in FIG. 8, the requested regenerative torque is continuously set even after the power generation amount reduction control is executed at time T24, and the traveling mode is the power generation mode even after time T24.
- the vehicle 6 In the initial state (before time T01), the vehicle 6 is stopped, and the rotating electrical machine 12 is generating electric power by the internal combustion engine torque Te in the directly engaged state of the first clutch C1 and the released state of the second clutch C2.
- the vehicle start condition for starting the vehicle 6 is satisfied at time T01, control is performed so that both the engagement pressure of the first clutch C1 and the engagement pressure of the second clutch C2 are slip engagement pressures ( Time T01-T02).
- the vehicle start condition can be established when, for example, an accelerator pedal depression operation, a brake pedal release operation, or the like by the driver is detected.
- the travel mode shifts to the first control mode time T02
- the first mode shift control is started.
- the selection target amount B0 is less than the selection reference value D0, and the first mode transition via the third control mode is performed. Is done. Also, although not shown in the figure, in this example, during the realization of the first control mode, the execution conditions (steps # 23 and # 24 in FIG. 4) of the wheel transmission driving force reduction control described above and the power generation amount reduction control are described. Is assumed that the execution condition (step # 33 in FIG. 5) is not satisfied.
- the second clutch C2 in the slip engagement state is controlled by torque control based on the target transmission torque capacity.
- the target transmission torque capacity is set according to the position of the second clutch C2 in the power transmission path so that the required driving force Td is transmitted to the wheels 15.
- the first clutch C1 in the slip engagement state is controlled (rotational speed control) by rotational speed feedback control so that the rotational speed of the internal combustion engine 11 follows the target rotational speed.
- the target rotation speed is set to a value equal to or higher than the lower limit rotation speed at which the internal combustion engine 11 can continue the independent operation (for example, an idle rotation speed or a value higher than the idle rotation speed).
- the target rotational speed is set to the rotational speed of the internal combustion engine 11 at the start of the first control mode (time T02), and is maintained at the rotational speed during the realization of the first control mode.
- the rotating electrical machine 12 is controlled by rotational speed control based on the target rotational speed.
- the target rotational speed is set to a value that is higher than the converted rotational speed and lower than the rotational speed of the internal combustion engine 11 and that can secure the required power generation amount even when the rotational speed is the lowest.
- the target rotational speed is set so that the difference from the converted rotational speed is constant. Therefore, as shown in FIG. 6, the rotational speed difference between the internal combustion engine 11 and the rotating electrical machine 12 decreases as the vehicle speed (converted rotational speed) increases.
- the rotating electrical machine torque Tm is set based on a value (required regenerative torque) obtained by dividing the required power generation amount by the target rotational speed.
- the slip-engaged second clutch C2 is controlled by torque control as in the first control mode.
- the rotating electrical machine 12 is also controlled by the rotational speed control in the same way as when the first control mode is realized, and the target rotational speed at this time is set so that the difference from the converted rotational speed gradually decreases.
- the difference between the rotation speed of the rotating electrical machine 12 and the converted rotation speed becomes equal to or less than a predetermined synchronization determination reference value at time T05
- the engagement pressure of the second clutch C2 is increased toward the complete engagement pressure.
- the second clutch C2 shifts to the direct engagement state, so that the travel mode shifts from the third control mode to the second control mode.
- Each control executed from time T04 to time T06 corresponds to the control for shifting the second clutch C2 to the direct engagement state, which is executed in step # 05 of FIG. 2 described above.
- the transition to the direct engagement state (time T03 to T04) of the first clutch C1 is performed in the slip engagement state of the second clutch C2. Is transmitted to the wheel 15. Further, in this example, since the period in which the rotating electrical machine 12 generates power in the slip engagement state of the first clutch C1 is only when the first control mode is realized, it results from torque transmission via the first clutch C1. It is also possible to increase energy generation efficiency by reducing energy loss.
- this specific example is different from the first specific example (FIG. 6), and is a specific example of the first mode transition via the fourth control mode. It is.
- the present specific example will be described focusing on differences from the first specific example. Points that are not particularly described are the same as those in the first specific example.
- the traveling mode becomes the first control mode, and the first mode transition control is started.
- the selection target amount B0 is not less than the selection reference value D0, and the first mode transition via the fourth control mode is performed. Is done.
- the target rotational speed of the rotating electrical machine 12 is set to a constant value. Therefore, as the vehicle speed (converted rotation speed) increases, the difference between the rotation speed of the rotating electrical machine 12 and the converted rotation speed decreases.
- the difference between the rotation speed of the rotating electrical machine 12 and the converted rotation speed becomes equal to or less than a predetermined synchronization determination reference value at time T13, the engagement pressure of the second clutch C2 is increased toward the complete engagement pressure. Then, at time T14, the second clutch C2 shifts to the direct engagement state, so that the travel mode shifts from the first control mode to the fourth control mode.
- Each control executed from time T12 to time T14 corresponds to control for shifting the second clutch C2 to the direct engagement state, which is executed in step # 07 of FIG. 2 described above.
- the first clutch C1 in the slip engagement state is controlled by rotational speed control in the same manner as when the first control mode is realized.
- the target rotational speed of the rotating electrical machine 12 is set so that the difference from the rotational speed of the internal combustion engine 11 gradually decreases.
- the engagement pressure of the first clutch C1 is increased toward the complete engagement pressure.
- the travel mode shifts from the fourth control mode to the second control mode.
- this specific example is different from the second specific example (FIG. 7) in that it is a specific example of the first mode transition via the fourth control mode. Although coincident, the wheel driving force reduction control and the power generation amount reduction control are executed during the realization of the first control mode, which is different from the second specific example.
- the present specific example will be described focusing on differences from the second specific example. Points that are not particularly described are the same as those in the first and second specific examples.
- all target amounts B are temperatures. Since the selection target amount B0 is equal to or greater than the selection reference value D0 when the first mode transition is executed (time T22), the first mode transition via the fourth control mode is performed. While the first control mode is being realized, each control is executed in the same manner as in the second specific example.
- the first determination target amount B1 is equal to or greater than the first determination reference value D1
- the second determination reference value D2 is more than 2nd determination reference value D2.
- wheel transmission driving force reduction control is executed, and the internal combustion engine torque Te is reduced so that the wheel transmission driving force becomes smaller than the required driving force Td. At this time, since the rotating electrical machine torque Tm is kept constant, the wheel transmission driving force is reduced from the required driving force Td in accordance with the reduction in the internal combustion engine torque Te.
- the first determination target amount B1 is equal to or greater than the third determination reference value D3.
- the power generation amount reduction control is executed, and the rotating electrical machine torque Tm (more precisely, the absolute value of the rotating electrical machine torque Tm) is reduced from the required regenerative torque, and the internal combustion engine torque Te is reduced according to the reduction amount. .
- the wheel transmission driving force does not change before and after the execution of the power generation amount reduction control.
- the rotating electrical machine 12 may be configured to continue power generation by the rotating electrical machine torque Tm reduced by the execution of the power generation amount reduction control, but in this example, the rotating electrical machine torque Tm is set to zero by the power generation amount reduction control.
- the power generation by the rotating electrical machine 12 is stopped. Thereafter, the same control as in the second specific example is performed.
- Each of times T25, T26, T27, and T28 in this example corresponds to times T13, T14, T15, and T16 in the second specific example (FIG. 7).
- the first determination target amount B1 is equal to or greater than the third determination reference value D3 during the realization of the first control mode. If not, only wheel transmission driving force reduction control is executed. Further, in the configuration in which the first determination reference value D1 is set to a value larger than the third determination reference value D3, not both the wheel transmission driving force decrease control and the power generation amount decrease control during the realization of the first control mode. In some cases, only the power generation amount reduction control is executed.
- Second Mode Transition This specific example is a specific example of the second mode transition executed when the vehicle 6 is stopped from the state of traveling in the second control mode, as shown in FIG. It is. Note that the same control can be performed when the vehicle 6 continues to travel in the first control mode after the execution of the second mode transition (the same applies to FIG. 10).
- the vehicle 6 In an initial state (before time T31), the vehicle 6 is traveling in the second control mode, and the rotating electrical machine 12 generates electric power with the internal combustion engine torque Te in a state where both the first clutch C1 and the second clutch C2 are directly connected. ing. And if the vehicle stop condition for stopping the vehicle 6 is satisfied at time T31, the second mode transition control is started.
- the vehicle stop condition may be established when, for example, an accelerator pedal release operation or a brake pedal depression operation by the driver is detected.
- the selection target amount B0 is less than the selection reference value D0 at the start of execution of the second mode transition control (time T31), and the second mode transition via the third control mode is performed. Is done. Therefore, in this example, the engagement pressure of the second clutch C2 is reduced to the slip engagement pressure at time T31. Thereby, the second clutch C2 shifts to the slip engagement state, and the travel mode shifts from the second control mode to the third control mode.
- the control for lowering the engagement pressure of the second clutch C2 executed at time T31 is executed in step # 13 of FIG. 3 described above for shifting the second clutch C2 to the slip engagement state. It corresponds to.
- the second clutch C2 in the slip engagement state is controlled by torque control based on the target transmission torque capacity.
- the target transmission torque capacity is set according to the position of the second clutch C2 in the power transmission path so that the required driving force Td is transmitted to the wheels 15.
- the rotating electrical machine 12 is controlled by rotational speed control based on the target rotational speed.
- the target rotational speed is a value that is higher than the converted rotational speed and equal to or higher than the lower limit rotational speed at which the internal combustion engine 11 can continue the independent operation (for example, a value higher than the idle rotational speed or the idle rotational speed). It is set to a value that can secure the amount of power generation.
- the target rotation speed is set to the rotation speed of the rotating electrical machine 12 at the start of the third control mode (time T31), and is maintained at the rotation speed while the third control mode is realized. Therefore, as the vehicle speed (converted rotational speed) decreases, the difference between the rotational speed of the rotating electrical machine 12 and the converted rotational speed increases.
- the slip-engaged second clutch C2 is controlled by torque control as in the third control mode.
- the first clutch C1 in the slip engagement state is controlled (rotational speed control) by rotational speed feedback control so that the rotational speed of the internal combustion engine 11 follows the target rotational speed.
- the target rotation speed is set to a value equal to or higher than the lower limit rotation speed at which the internal combustion engine 11 can continue the independent operation (for example, an idle rotation speed or a value higher than the idle rotation speed).
- the target rotational speed is set to the rotational speed of the internal combustion engine 11 at the start of the first control mode (time T32), and is maintained at the rotational speed during the realization of the first control mode.
- the rotating electrical machine 12 is controlled by the rotational speed control in the same way as when the third control mode is realized.
- the target rotational speed at this time is higher than the converted rotational speed and the rotational speed of the internal combustion engine 11.
- the lower value is set to a value that can secure the required power generation amount.
- the target rotational speed is set so that the difference from the converted rotational speed is constant. Therefore, as shown in FIG. 9, the target rotational speed of the rotating electrical machine 12 decreases as the vehicle speed (converted rotational speed) decreases, and the target rotational speed is maintained at a constant value after time T33 when the vehicle 6 stops. Is done.
- step # 23 and # 24 in FIG. 4 After the transition to the first control mode (after time T32), the above-described wheel transmission driving force reduction control execution conditions (steps # 23 and # 24 in FIG. 4) and the power generation amount reduction control are executed. It is assumed that the condition (step # 33 in FIG. 5) is not satisfied.
- this specific example is different from the first specific example (FIG. 9), and is a specific example of the second mode transition via the fourth control mode. It is.
- the present specific example will be described focusing on differences from the first specific example. Points that are not particularly described are the same as those in the first specific example.
- the selection target amount B0 is greater than or equal to the selection reference value D0, and the second mode transition via the fourth control mode is performed. Is done. Therefore, in this example, at time T41, the engagement pressure of the first clutch C1 is reduced to the slip engagement pressure. Thereby, the first clutch C1 shifts to the slip engagement state, and the travel mode shifts from the second control mode to the fourth control mode.
- the control for lowering the engagement pressure of the first clutch C1 executed at the time T41 is executed in step # 17 of FIG. 3 described above for controlling the first clutch C1 to the slip engagement state. It corresponds to.
- the first clutch C1 in the slip engagement state is controlled (rotational speed) by rotational speed feedback control so that the rotational speed of the internal combustion engine 11 follows the target rotational speed.
- Speed control the target rotation speed is set to a value equal to or higher than the lower limit rotation speed at which the internal combustion engine 11 can continue the independent operation (for example, an idle rotation speed or a value higher than the idle rotation speed).
- the target rotational speed is set to the rotational speed of the internal combustion engine 11 at the start of the fourth control mode (time T41), and during the realization of the fourth control mode and the subsequent realization of the first control mode, The rotation speed is maintained. Therefore, as shown in FIG. 10, the rotational speed difference between the internal combustion engine 11 and the rotating electrical machine 12 increases as the vehicle speed (converted rotational speed) decreases.
- the first clutch C1 in the slip engagement state is controlled by the rotational speed control as in the case of realizing the fourth control mode.
- the slip-engaged second clutch C2 is controlled by torque control based on the target transmission torque capacity.
- the target transmission torque capacity is set according to the position of the second clutch C2 in the power transmission path so that the required driving force Td is transmitted to the wheels 15.
- the rotating electrical machine 12 is controlled by rotational speed control based on the target rotational speed.
- the target rotational speed is set to a value that is higher than the converted rotational speed and lower than the rotational speed of the internal combustion engine 11 and that can secure the required power generation amount.
- this target rotational speed is set to a constant value. Therefore, as shown in FIG. 10, as the vehicle speed (converted rotational speed) decreases, the difference between the rotational speed of the rotating electrical machine 12 and the converted rotational speed increases, and after time T43 when the vehicle 6 stops, the rotating electrical machine 12 The difference between the rotation speed and the converted rotation speed is constant.
- the configuration in which the torque correction control unit 54 executes the two torque correction controls of the first torque correction control and the second torque correction control in parallel has been described as an example.
- the embodiment of the present invention is not limited to this, and any one of a configuration that executes only one of the first torque correction control and the second torque correction control, or any of the first torque correction control and the second torque correction control. It is also possible to adopt a configuration in which neither is executed.
- the mode transition is executed through the third control mode.
- the configuration is described in which the mode transition is performed through the fourth control mode when the selection target amount B0 is equal to or greater than the selection reference value D0.
- the embodiment of the present invention is not limited to this.
- the case where the selection target amount B0 is less than the selection reference value D0 is the third. It is also possible to adopt a configuration in which the mode transition is executed through the control mode and the mode transition is executed through the fourth control mode when the selection target amount B0 is equal to or larger than the selection reference value D0.
- the other mode transition can be configured such that the travel mode through which the mode passes is fixed.
- the travel mode that passes through may be a travel mode that is different from the third control mode or the fourth control mode.
- the determination as to which mode transition is to be executed via the third control mode or the fourth control mode is the execution of the first mode transition control or the second mode transition control.
- the configuration executed at the start has been described as an example.
- the embodiment of the present invention is not limited to this, and the determination of the magnitude relationship between the selection target amount B0 and the selection reference value D0 is also executed during the mode transition control, and the magnitude relationship is reversed. In such a case, it is possible to adopt a configuration in which the traveling mode through which the route passes is switched.
- the configuration in which one of the gear shifting engagement devices (second clutch C2) in the speed change mechanism 13 is the “second engagement device” has been described as an example.
- the embodiment of the present invention is not limited to this. That is, in the power transmission path connecting the internal combustion engine 11 and the wheel 15, if the engagement device is provided on the wheel 15 side of the rotating electrical machine 12, the other engagement device in the speed change mechanism 13 is “second engagement”. It may be a combined device.
- a fluid coupling such as a torque converter
- a lock-up clutch included in the fluid coupling may be used as the “second engagement device”.
- a dedicated transmission clutch may be provided between the rotating electrical machine 12 and the wheel 15 and the transmission clutch may be a “second engagement device”.
- an automatic continuously variable transmission mechanism, a manual stepped transmission mechanism, a fixed transmission mechanism, or the like can be used as the transmission mechanism 13. Further, the position of the transmission mechanism 13 can also be set arbitrarily.
- the configuration in which the first clutch C1 and the second clutch C2 are hydraulically driven engagement devices in which the engagement pressure is controlled according to the supply hydraulic pressure has been described as an example.
- the embodiment of the present invention is not limited to this. That is, it is only necessary that the transmission torque capacity can be adjusted according to the increase or decrease of the engagement pressure.
- one or both of them can be controlled by electromagnetic engagement in which the engagement pressure is controlled according to the electromagnetic force. It is good also as an apparatus.
- the configuration in which the internal combustion engine control device 30 is provided separately from the control device 40 has been described as an example.
- the embodiment of the present invention is not limited to this, and the internal combustion engine control device 30 may be integrated with the control device 40.
- the assignment of the function units in the control device 40 described in the above embodiment is merely an example, and a plurality of function units can be combined or one function unit can be further divided.
- the present invention controls a vehicle drive device in which a first engagement device, a rotating electrical machine, and a second engagement device are provided in order from the internal combustion engine side in a power transmission path that connects the internal combustion engine and wheels. It can utilize suitably for the control apparatus.
- driving device 11 internal combustion engine 12: rotating electrical machine 15: wheel 40: control device 51: target amount acquisition unit 52: mode control unit B0: selection target amount B1: first determination target amount B2: second determination target amount D0 : Selection reference value D1: First determination reference value D2: Second determination reference value D3: Third determination reference value C1: First clutch (first engagement device) C2: Second clutch (second engagement device) Td: Required driving force
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Abstract
Description
また、「直結係合状態」は、対象となる係合装置によって係合される2つの係合部材が一体回転する状態で係合されている状態を表し、「スリップ係合状態」は、当該2つの係合部材が回転速度差を有する状態で駆動力を伝達可能に係合されている状態を表す。
そして、上記の特徴構成によれば、第一制御モードと第二制御モードとの間の少なくとも何れか一方向側のモード移行に際し、選択対象量と選択基準値との間の大小関係に基づき第二係合装置の発熱状態を推定して、経由するモードを第三制御モード及び第四制御モードの中から適切に選択することができる。すなわち、第二係合装置の温度上昇が許容される場合には、内燃機関のトルクを直接回転電機に伝達できる第三制御モードを選択してエネルギ効率の向上を図り、そうでない場合には、第四制御モードを選択して第二係合装置の発熱量を抑制することができる。これにより、第二係合装置を保護しつつ、所望の発電量を確保することを容易とする第一制御モードへの移行又は当該第一制御モードから他モードへの移行を適切に実行することができる。
本実施形態に係る制御装置40による制御対象となる駆動装置1は、いわゆる1モータパラレル方式のハイブリッド車両用の駆動装置として構成されている。図1に示すように、この駆動装置1は、内燃機関11と車輪15とを結ぶ動力伝達経路に、内燃機関11の側から順に、第一クラッチC1、回転電機12、及び第二クラッチC2(変速機構13)を備えている。すなわち、内燃機関11と車輪15とを結ぶ動力伝達経路に回転電機12が設けられていると共に、内燃機関11と回転電機12との間に第一クラッチC1が設けられ、回転電機12と車輪15との間に第二クラッチC2(変速機構13)が設けられている。
図1に示すように、本実施形態に係る制御装置40は、走行モード決定部41、要求駆動力決定部42、回転電機制御部43、第一クラッチ動作制御部44、変速機構動作制御部45、対象量取得部51、モード制御部52、対象量判定部53、及びトルク補正制御部54を備えている。これらの各機能部は、互いに情報の受け渡しを行うことができるように構成されている。
走行モード決定部41は、車両6の走行モードを決定する機能部である。走行モード決定部41は、例えば車速やアクセル開度、蓄電装置28の蓄電量等に基づいて、所定のマップ(モード選択マップ)を参照する等して駆動装置1が実現すべき走行モードを決定する。
要求駆動力決定部42は、車両6を走行させるべく車輪15を駆動するために要求される要求駆動力Tdを決定する機能部である。要求駆動力決定部42は、車速とアクセル開度とに基づいて、所定のマップ(要求駆動力決定マップ)を参照する等して要求駆動力Tdを決定する。このようにして決定される要求駆動力Tdは、基本的に、運転者の人為的な操作(例えばアクセル操作等)に応じた挙動を実現するために必要な駆動力と等しくなる。決定された要求駆動力Tdに基づき、内燃機関11及び回転電機12のそれぞれが受け持つ分担駆動力が、各分担駆動力の和が要求駆動力Tdに等しくなるように決定される。そして、決定された分担駆動力が車輪15に伝達されるように、内燃機関制御装置30による内燃機関11の制御、及び回転電機制御部43による回転電機12の制御が実行される。これにより、車輪15には基本的に、要求駆動力Tdと同じ大きさの駆動力が伝達される。
回転電機制御部43は、回転電機12の動作制御を行う機能部である。回転電機制御部43は、インバータ装置27を制御することで回転電機12の動作点(回転電機トルクTm及び回転速度)を制御する。本実施形態では、回転電機制御部43は、車両6の走行状態に応じて回転電機12のトルク制御と回転速度制御とを切り替えことが可能である。ここで、トルク制御は、制御目標として目標トルクを設定し、回転電機トルクTmをその目標トルクに追従させる(近づける)制御である。また、回転速度制御は、制御目標として目標回転速度を設定し、回転電機トルクTmを制御して回転電機12の回転速度をその目標回転速度に追従させる制御である。
第一クラッチ動作制御部44は、第一クラッチC1の動作制御を行う機能部である。ここで、第一クラッチ動作制御部44は、油圧制御装置25を介して第一クラッチC1に供給される油圧を制御し、第一クラッチC1の係合圧を制御することにより、当該第一クラッチC1の動作制御を行う。具体的には、係合圧を解放境界圧未満(例えば解放圧)とすることにより第一クラッチC1を解放状態とし、係合圧を係合境界圧以上(例えば完全係合圧)とすることにより第一クラッチC1を直結係合状態とする。また、係合圧を解放境界圧以上係合境界圧未満のスリップ係合圧とすることにより、第一クラッチC1をスリップ係合状態とする。
変速機構動作制御部45は、変速機構13の動作制御を行う機能部である。変速機構動作制御部45は、アクセル開度及び車速に基づいて、所定のマップ(変速マップ)を参照する等して目標変速段を決定する。そして、変速機構動作制御部45は、決定された目標変速段に基づいて、変速機構13内に備えられる所定のクラッチ及びブレーキ等への供給油圧を制御して目標変速段を形成する。
対象量取得部51は、係合装置の発熱状態に関する物理量である対象量Bを取得する機能部である。具体的には、対象量取得部51は、第二クラッチC2の温度及び発熱量の少なくとも一方を選択対象量B0として取得し、本実施形態では更に、対象量取得部51は、第一クラッチC1の温度及び発熱量の少なくとも一方を第一判定対象量B1として取得するとともに、第二クラッチC2の温度及び発熱量の少なくとも一方を第二判定対象量B2として取得する。なお、選択対象量B0と第二判定対象量B2とは、互いに同一の物理量としても互い異なる物理量としても良い。
対象量判定部53は、対象量取得部51が取得した対象量Bを、当該対象量Bについての基準値D(判定基準値)と比較して大小関係を判定する機能部である。本実施形態では、対象量取得部51は、対象量Bとして選択対象量B0、第一判定対象量B1、及び第二判定対象量B2の3つを取得するため、対象量判定部53はこれら3つの対象量Bのそれぞれについて、対応する基準値Dとの間で大小関係の判定を行う。
モード制御部52は、第一クラッチ動作制御部44や第二クラッチ動作制御部45a等の他の機能部を協調制御することで、走行モード決定部41が決定する各走行モードを切り替えて当該各モードを実現する機能部である。上記のように、走行モード決定部41が選択可能な走行モードには、第一制御モード、第二制御モード、第三制御モード、及び第四制御モードが含まれるため、モード制御部52は、第一制御モードと、第二制御モードと、第三制御モードと、第四制御モードと、を切り替えることができる。
モード制御部52を中核として実行される第一モード移行制御の処理手順について、図2のフローチャートを参照して説明する。なお、第一モード移行制御の実行開始時には第一制御モードが実現されているため、第一クラッチC1及び第二クラッチC2の双方はスリップ係合状態にある。
次に、モード制御部52を中核として実行される第二モード移行制御の処理手順について、図3のフローチャートを参照して説明する。なお、第二モード移行制御の実行開始時には第二制御モードが実現されているため、第一クラッチC1及び第二クラッチC2の双方は直結係合状態にある。
トルク補正制御部54は、トルク補正制御を実行する機能部である。このトルク補正制御では、所定の条件が成立した際に内燃機関トルクTeを低下させるトルク低下制御を実行する。本実施形態では、トルク補正制御部54は、第一トルク補正制御及び第二トルク補正制御の2つのトルク補正制御を並行して実行する。
上記のような構成を備える制御装置40において実行される第一モード移行の具体例について、図6から図8のタイムチャートを参照して順に説明する。なお、各タイムチャートにおいて、「同期線(換算回転速度)」は、変速機構13において変速段(本例では第1速段)が形成されていると仮定した場合の、出力軸Oの回転速度を中間軸Mの回転速度に換算して得られる回転速度を表し、「要求駆動力」は、要求駆動力Tdを当該変速段に対応する変速比で除算した値で示している。
本具体例は、図6に示すように、車両6が停止(換算回転速度が零)しているとともに回転電機12に発電を行わせている状態から車両6を発進させる際に実行される第一モード移行の具体例である。なお、第一モード移行制御の実行開始時に車両6が走行中である場合にも同様の制御を行うことが可能である(図7、図8についても同様)。
本具体例は、図7に示すように、上記第一の具体例(図6)とは異なり、第四制御モードを経由する第一モード移行の具体例である。以下、本具体例について、上記第一の具体例との相違点を中心に説明する。特に説明しない点については、上記第一の具体例と同様とする。
本具体例は、図8に示すように、第四制御モードを経由する第一モード移行の具体例という点では上記第二の具体例(図7)と一致するが、第一制御モードの実現中に車輪駆動力低下制御と発電量低下制御とが実行されるという点で、上記第二の具体例とは異なる。以下、本具体例について、上記第二の具体例との相違点を中心に説明する。特に説明しない点については、上記第一及び第二の具体例と同様とする。
次に、制御装置40において実行される第二モード移行の具体例について、図9、図10のタイムチャートを参照して順に説明する。
本具体例は、図9に示すように、第二制御モードで走行している状態から車両6を停車させる際に実行される第二モード移行の具体例である。なお、第二モード移行の実行後に車両6が第一制御モードで走行を継続する場合にも同様の制御を行うことが可能である(図10についても同様)。
本具体例は、図10に示すように、上記第一の具体例(図9)とは異なり、第四制御モードを経由する第二モード移行の具体例である。以下、本具体例について、上記第一の具体例との相違点を中心に説明する。特に説明しない点については、上記第一の具体例と同様とする。
最後に、本発明に係る制御装置の、その他の実施形態について説明する。なお、以下のそれぞれの実施形態で開示される構成は、矛盾が生じない限り、他の実施形態で開示される構成と組み合わせて適用することも可能である。
また、例えば回転電機12と車輪15との間にトルクコンバータ等の流体継手を備える場合において、当該流体継手が有するロックアップクラッチを「第二係合装置」としても良い。或いは、例えば回転電機12と車輪15との間に専用の伝達クラッチを設け、当該伝達クラッチを「第二係合装置」としても良い。これらの場合には、変速機構13として、自動無段変速機構、手動有段変速機構、及び固定変速機構等を用いることもできる。また、変速機構13の位置も任意に設定することができる。
11:内燃機関
12:回転電機
15:車輪
40:制御装置
51:対象量取得部
52:モード制御部
B0:選択対象量
B1:第一判定対象量
B2:第二判定対象量
D0:選択基準値
D1:第一判定基準値
D2:第二判定基準値
D3:第三判定基準値
C1:第一クラッチ(第一係合装置)
C2:第二クラッチ(第二係合装置)
Td:要求駆動力
Claims (3)
- 内燃機関と車輪とを結ぶ動力伝達経路に、前記内燃機関の側から順に、第一係合装置、回転電機、及び第二係合装置、が設けられた車両用駆動装置を制御対象とする制御装置であって、
前記第一係合装置及び前記第二係合装置の双方のスリップ係合状態で前記回転電機に発電を行わせる第一制御モードと、前記第一係合装置及び前記第二係合装置の双方の直結係合状態で前記回転電機に発電を行わせる第二制御モードと、前記第一係合装置の直結係合状態且つ前記第二係合装置のスリップ係合状態で前記回転電機に発電を行わせる第三制御モードと、前記第一係合装置のスリップ係合状態且つ前記第二係合装置の直結係合状態で前記回転電機に発電を行わせる第四制御モードと、を切り替えるモード制御部と、
前記第二係合装置の温度及び発熱量の少なくとも一方を選択対象量として取得する対象量取得部と、を備え、
前記モード制御部は、前記第一制御モードから前記第二制御モード及び前記第二制御モードから前記第一制御モードの少なくとも一方のモード移行に際し、前記選択対象量が予め定められた選択基準値未満である場合は前記第三制御モードを経て前記モード移行を実行し、前記選択対象量が前記選択基準値以上である場合には前記第四制御モードを経て前記モード移行を実行する制御装置。 - 前記対象量取得部は、前記第一係合装置の温度及び発熱量の少なくとも一方を第一判定対象量として取得するとともに、前記第二係合装置の温度及び発熱量の少なくとも一方を第二判定対象量として取得し、
前記第一制御モードにおいて、前記第一判定対象量が予め定められた第一判定基準値未満であり、且つ前記第二判定対象量が予め定められた第二判定基準値未満である場合には、前記車輪を駆動するために要求される要求駆動力が当該車輪に伝達されるように前記要求駆動力に応じた制御を実行し、
前記第一制御モードにおいて、前記第一判定対象量が前記第一判定基準値以上であり、且つ前記第二判定対象量が前記第二判定基準値以上である場合には、前記車輪に伝達される駆動力が前記要求駆動力より小さくなるように、前記内燃機関の出力トルクを低下させる制御を実行する請求項1に記載の制御装置。 - 前記対象量取得部は、前記第一係合装置の温度及び発熱量の少なくとも一方を第一判定対象量として取得し、
前記第一制御モードにおいて、前記第一判定対象量が予め定められた第三判定基準値以上となった場合には、前記回転電機の出力トルクを低下させることで当該回転電機による発電量を低下させるとともに、前記回転電機の出力トルクの低下分に応じて前記内燃機関の出力トルクを低下させる制御を実行する請求項1又は2に記載の制御装置。
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CN103596826B (zh) | 2016-06-15 |
CN103596826A (zh) | 2014-02-19 |
JP2013035416A (ja) | 2013-02-21 |
DE112012001939T5 (de) | 2014-02-13 |
US20140094342A1 (en) | 2014-04-03 |
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